WO2007140751A2 - Convertisseur de couple avec turbine brasée - Google Patents

Convertisseur de couple avec turbine brasée Download PDF

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Publication number
WO2007140751A2
WO2007140751A2 PCT/DE2007/000980 DE2007000980W WO2007140751A2 WO 2007140751 A2 WO2007140751 A2 WO 2007140751A2 DE 2007000980 W DE2007000980 W DE 2007000980W WO 2007140751 A2 WO2007140751 A2 WO 2007140751A2
Authority
WO
WIPO (PCT)
Prior art keywords
inner ring
blade
torque converter
turbine
slot
Prior art date
Application number
PCT/DE2007/000980
Other languages
German (de)
English (en)
Other versions
WO2007140751A3 (fr
Inventor
Donald Mccullick
Christopher Sidor
Joachim Hoffmann
Chad Keets
Patanjali Peri
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112007001236T priority Critical patent/DE112007001236A5/de
Priority to JP2009513544A priority patent/JP2009540224A/ja
Publication of WO2007140751A2 publication Critical patent/WO2007140751A2/fr
Publication of WO2007140751A3 publication Critical patent/WO2007140751A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/28—Details with respect to manufacture, e.g. blade attachment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/26—Shape of runner blades or channels with respect to function

Definitions

  • the invention generally relates to a turbine for a torque converter, and more particularly to a turbine having vanes that are partially brazed to an inner ring of the turbine to reduce the noise caused by the entirety of the mechanical and hydrodynamic properties of the turbine subassembly.
  • FIG. 1 illustrates, in a general block diagram, the relationship between the engine 7, the torque converter 10, the transmission 8, and the differential / axle assembly 9 in a typical vehicle.
  • the three major components of the torque converter are the pump 37, the turbine 38 and the stator 39.
  • the torque converter becomes a sealed chamber when the pump is welded to the lid 11.
  • the cover is connected to the converter driver disk (Fiexplate) 41, which in turn is bolted to the crankshaft 42 of the motor 7.
  • the lid may be connected to the transducer driver disc using lands or pegs welded to the lid.
  • the welded connection between the pump and the cover transfers the motor torque to the pump. Therefore, the pump always rotates at the engine speed.
  • the function of the pump is to use this rotational movement to move the fluid radially outward and axially to the turbine.
  • the pump serves as a centrifugal pump, which conveys the liquid from a small radial inlet to a large radial outlet, thus increasing the energy of the liquid.
  • the pressure for engaging the transmission clutches and the converter clutch is generated by an additional pump in the transmission, which is driven by the pump hub.
  • a fluid circuit is formed by the pump (sometimes referred to as an impeller), the turbine and the stator (sometimes referred to as a reactor).
  • the fluid circuit allows the engine to continue running when the vehicle stops and accelerate the vehicle again when desired by a driver. Similar to a gear reduction, the torque converter supports engine torque through a torque ratio.
  • the torque ratio is the ratio of output torque to input torque.
  • the torque ratio is highest when the turbine speed is low or zero (also referred to as stalling).
  • the stall torque ratios are usually in the range of 1.8 to 2.2. This means that the output torque of the torque converter is 1.8 to 2.2 times larger than the drive torque.
  • the output speed is much lower than the input speed because the turbine is connected to the output side and does not rotate while the drive side is running at engine speed.
  • the turbine 38 utilizes the energy received by the fluid from the pump 37 to drive the vehicle.
  • the turbine housing 22 is connected to the turbine hub 19.
  • the turbine hub 19 transmits the torque of the turbine to the drive shaft 43 of the transmission via a spline connection.
  • the drive shaft is connected via gears and shafts in the transmission 8 and an axle differential 9 with the wheels of the vehicle.
  • the force of the liquid acting on the turbine blades is delivered by the turbine in the form of a torque.
  • Axial thrust bearings 31 absorb the axial forces applied to the components by the fluid. Once the output torque is sufficient to overcome the inertia of the stationary vehicle, the vehicle starts moving.
  • the stator 39 serves to redirect the liquid to contribute to the acceleration of the pump and thereby increase the torque ratio.
  • the stator 39 is connected by a freewheel 46 with the stator shaft 45.
  • the stator shaft is connected to the transmission housing 47 and does not rotate. Free wheel 46 prevents stator 39 from rotating at low speed ratios (when the pump is turning faster than the turbine).
  • the From the turbine outlet 44 into the stator 39 entering liquid is deflected by the stator blades 48, so that it enters the pump 37 in the direction of rotation.
  • Design parameters include the torque ratio, efficiency, and ability of the torque converter to absorb engine torque without the engine "spinning.” This occurs when the torque converter is too small and the pump can not decelerate the engine.
  • the torque converter works satisfactorily by letting the engine run while the vehicle is stationary, and by assisting engine torque to increase performance.
  • the torque converter is less effective.
  • the torque ratio of the torque converter returns from a high level of approximately 1.8 to 2.2 to a torque ratio of approximately one.
  • the torque ratio of 1 is referred to as the coupling point.
  • the liquid entering the stator does not need to be redirected, and the free-wheel in the stator allows for rotation in the same direction as the pump and turbine. Since the stator does not deflect the fluid, the torque output by the torque converter is equal to the torque absorbed.
  • the entire fluid circuit turns as a unit.
  • a torque converter clutch 49 is used for mechanical connection of the drive side with the output side of the torque converter, which increases the efficiency to almost 100%.
  • the clutch piston plate 17 is hydraulically operated by commands from the transmission control.
  • the piston plate 17 is sealed at its inner diameter by an O-ring 18 against the turbine hub 19 and at its outer diameter by a ring 51 made of friction material against the lid 11. These seals form a pressure chamber and press the piston plate 17 against the cover 11. This mechanical connection bypasses the fluid circuit of the torque converter.
  • the mechanical connection of the torque converter clutch 49 transmits significantly more torsional variations to the powertrain. Since the powertrain is basically a spring-mass system, torsional variations from the engine can excite resonant vibrations of the system. To remove the resonance vibrations of the drive train from the driving range, a damper is used.
  • the damper includes serially arranged springs 15 to reduce the effective spring rate of the system and thus the resonant frequency.
  • the converter clutch 49 generally comprises four components: a piston plate 17, cover plates 12 and 16, springs 15 and a flange 13.
  • the cover plates 12 and 16 transmit the torque from the piston plate 17 to the compression springs 15.
  • On the cover plate are around the springs 15th around lugs 52 are formed to support the springs in the axial direction.
  • the torque is transmitted via a riveted connection from the piston plate 17 to the cover plates 12 and 16.
  • the cover plates 12 and 16 allow the torque to act on the compression springs 15 by contact with an edge of a recess for the spring.
  • the two cover plates together support the spring on both sides of its central axis.
  • the spring force is transmitted to the flange 13 by contact with an edge of the recess for the flange spring.
  • the flange also has a non-rotatable tongue or a rotationally fixed slot which engages a portion of the cover plate to prevent excessive compression of the springs during transmission of high torques.
  • the torque is transmitted from the flange 13 to the turbine hub 19 and to the drive shaft 43 of the transmission.
  • the hysteresis assembly generally consists of a diaphragm spring (or Belleville spring) 14 between the flange 13 and one of the cover plates 16 to urge the flange 13 against the other cover plate 12. By controlling the force exerted on the diaphragm spring 14, the friction torque can also be controlled. Typical hysteresis values are in the range of 10 to 30 Nm.
  • Converter turbines are generally formed with vanes disposed between an inner ring and a turbine housing.
  • the vanes direct a fluid from the inlet of the turbine, located near the outer edge of the turbine, to the outlet of the turbine, which is near the inner edge of the turbine.
  • the blades are usually attached to the inner ring with tabs that protrude from the blade and are bent over after being inserted into the slots in the inner ring.
  • the durability and performance of the turbine can be improved by incorporating a bonding material at the joint.
  • the joining material various materials may be considered, but because of the relatively narrow spaces between the blades and the surfaces of the housing and the inner ring, materials which can flow in by capillary action are preferable.
  • a connecting material usually a solder material such as solder paste is selected, but other alternatives can be used.
  • solder material such as solder paste
  • the rigidity of the transducer turbine is increased because the edges of the blades facing the inner race are bonded to the surfaces of the inner race.
  • the connecting material makes the turbine a compact unit consisting of three separate components.
  • Turbine assemblies of the type described above may experience noise due to the combination of mechanical and hydrodynamic properties of the turbine subassembly.
  • the noise generated in a turbine subassembly can be so strong that it bothers drivers.
  • the invention generally includes a torque converter including: an inner ring; a turbine blade connected to the inner ring and having an outer edge, wherein the outer edge includes a segment, the one Opposite outer surface of the inner ring and is arranged in the vicinity of the outer surface.
  • a bonding material serves to firmly connect at least a portion of the segment but less than the entirety of the segment to the outer surface of the inner ring. The segment is firmly connected to reduce the resonances in the turbine.
  • the inner ring includes an inner surface opposing the outer surface and at least one open path between the inner surface and the outer surface.
  • the at least one open path is aligned with the segment and the alignment is perpendicular to the outer surface of the inner ring.
  • the at least one open path is arranged to inhibit capillary action along the segment.
  • the inner ring includes first and second slots, the blade includes first and second tabs inserted into the first and second slots, respectively, and the at least one first or second slot includes the at least one open path.
  • each first or second slot includes the at least one open path.
  • the inner ring includes first and second slots
  • the blade includes first and second tabs inserted into the first and second slots, respectively, and the at least one open path is between the first and second slots arranged separately from these.
  • the inner ring includes first and second slots
  • the blade includes first and second tabs inserted into the first and second slots, respectively, and the segment includes a notch disposed between the first and second tabs. The notch is arranged to inhibit capillary action along the segment.
  • a solder material or a welding material serves as a bonding material.
  • the invention generally includes an inner ring for a torque converter that includes an outer surface and an interruption in the outer surface.
  • the break is arranged to inhibit the capillary action of a flowable bonding material introduced at a juncture between a turbine blade secured to the inner ring and the outer surface.
  • the inner ring includes a slot, and the Interruption touches the slot.
  • the interruption is in the form of an opening in the inner ring.
  • the invention generally includes a blade for a turbine in a torque converter that includes first and second tabs disposed on an edge of the blade to secure the blade to the inner ring of the torque converter.
  • the edge is arranged so that it is close to an outer surface of the inner ring when the blade is attached to the inner ring.
  • a notch is disposed in the edge to prevent the capillary action of the bonding material in a channel formed between the blade and the outer surface.
  • the invention generally includes a torque converter including an inner ring and a turbine blade connected to the inner ring, the blade having an edge proximate an outer surface of the inner ring. At least one channel is formed between the blade and the outer surface, wherein the connecting material at least partially, but not completely, fills the channel.
  • the invention generally includes a method of controlling the resonance of a turbine in a torque converter, the method comprising the steps of: placing a segment of an outer edge of the blade proximate an outer surface of an inner ring of the torque converter; Creating a channel between the segment and the outer surface; Creating an interruption in the channel to prevent capillary action in the channel; and introducing a flowable bonding material into the channel.
  • the method connects less than the entirety of the segment fixed to the outer surface.
  • the method combines the turbine blade with the inner ring.
  • a general object of the present invention is to provide a torque converter with a turbine blade having reduced resonance and rigidity.
  • FIG. 1 is a general block diagram illustrating power flow in a motor vehicle for explaining the position and function of a torque converter in its powertrain;
  • FIG. 2 is a cross-sectional view of a prior art torque converter in an installed position on an engine of a motor vehicle;
  • Fig. 3 is a left side view of the torque converter shown in Fig. 2 taken along line 3-3 in Fig. 2;
  • Fig. 4 is a cross-sectional view of the torque converter shown in Figs. 2 and 3 taken along section line 4-4 in Fig. 3;
  • Fig. 5 is an exploded, first exploded view of the torque converter shown in Fig. 2, as viewed from the left side of an observer of the torque converter;
  • FIG. 6 is an exploded, second exploded view of the torque converter shown in FIG. 2 as viewed from a right-side view of a torque converter observer;
  • FIG. 6 is an exploded, second exploded view of the torque converter shown in FIG. 2 as viewed from a right-side view of a torque converter observer;
  • Fig. 7A is a perspective view of a cylindrical coordinate system illustrating the spatial terms used in the present application.
  • Fig. 7B is a perspective view of an object in the cylindrical coordinate system of Fig. 7A illustrating the spatial terms used in the present application;
  • Fig. 8 is a rear view of the converter turbine according to the present invention having a plurality of blades according to the present invention
  • Fig. 9 is a rear view of the converter turbine shown in Fig. 8, in which the inner ring is removed;
  • Fig. 10 is a cross-sectional view of the wall turbine shown in Fig. 9 taken along section line 10-10 in Fig. 9;
  • Fig. 11 is a perspective view of a blade of the converter turbine according to the present invention.
  • Fig. 12 is a plan view of an inner ring according to the present invention.
  • Fig. 13 is a cross-sectional view of the inner ring shown in Fig. 12 taken along section line 13-13 in Fig. 12;
  • Fig. 14 is a perspective view of a turbine blade for use with an inner ring according to the present invention.
  • Fig. 15 is a rear view of an inner ring according to the present invention.
  • Fig. 7A is a perspective view of a cylindrical coordinate system 80 illustrating the spatial notation used in the present application.
  • the present invention will be described, at least in part, in connection with a cylindrical coordinate system.
  • the system 80 has a longitudinal axis 81 which serves as a reference for the following directional and spatial terms.
  • the attributes "axial,” “radial,” and “circumferential” refer to an orientation parallel to axis 81, to radius 82 (which is perpendicular to axis 81), and to circumference 83, respectively.
  • the attributes “axial,” “radial” and “perimeter” also refer to an orientation parallel to corresponding areas.
  • the objects 84, 85 and 86 serve to explain the position of the various planes.
  • the surface 87 of the object 84 forms an axial plane.
  • the axis 81 forms a line along the surface.
  • the surface 88 of the object 85 forms a radial plane. That is, the radius 82 forms a line along the surface.
  • the surface 89 of the object 86 forms a peripheral surface. That is, the periphery 83 forms a line along the surface.
  • an axial movement or position is parallel to axis 81
  • a radial movement or position is parallel to radius 82
  • a circumferential movement or length is parallel to circumference 83. Rotation is about axis 81.
  • the attributes “axial”, “radial” and “circumferential” also refer to an orientation parallel to the axis 81, the radius 82 and the circumference 83, respectively.
  • the attributes “axial”, “radial” and “circumferential” refer to one another to an orientation parallel to corresponding surfaces.
  • FIG. 7B is a perspective view of the object 90 in the cylindrical coordinate system 80 of FIG. 7A illustrating the spatial notation used in the present application.
  • the cylindrical object 90 is representative of a cylindrical object in a cylindrical coordinate system and should by no means be construed as limiting the present invention.
  • the object 90 includes an axial surface 91, a radial surface 92, and a peripheral surface 93.
  • the surface 91 is part of an axial plane
  • the surface 92 is part of a radial plane
  • the surface 93 is part of a peripheral surface.
  • FIG. 8 is a rear view of a converter turbine 100 in accordance with the present invention having a plurality of vanes 106 in accordance with the present invention.
  • FIG. 9 is a rear view of the converter turbine 100 shown in FIG. 8 with the inner ring removed.
  • FIG. 9 is a rear view of the converter turbine 100 shown in FIG. 8 with the inner ring removed.
  • FIG. 10 is a cross-sectional view of the converter turbine 100 shown in FIG. 9 in accordance with the present invention taken along section line 10-10 in FIG. 9.
  • FIG. 10 is a cross-sectional view of the converter turbine 100 shown in FIG. 9 in accordance with the present invention taken along section line 10-10 in FIG. 9.
  • FIG. 11 is a perspective view of the blade 106 of the converter turbine.
  • the turbine 100 includes a plurality of blades 106.
  • the blades 106 are commonly connected to the turbine housing 102 and the inner ring 104 to form the turbine 100.
  • the blades 106 are first connected to the inner ring using tabs, such as tabs 108 and 118.
  • the segment or edge 120 is the portion of the outer edge 103 of the blade that faces the outer surface of the inner ring 104. That is, the segment 120 is in the vicinity of the outer surface after installation of the blade using the tongues. At the juncture between edge 120 and the outer surface of inner ring 104, a gap or channel remains open.
  • a flowable bonding material is used to secure the turbine blades to an inner ring, with the bonding material distributed by capillary action across the joint. That is, the flowable material enters the channel.
  • the bonding material any material known in the art for bonding metal surfaces may be used, including, but not limited to, brazing material, welding material, or a similar metallic joining substance.
  • a solder paste is used to connect the blades 106 to the inner ring 104. The solder paste flows on heating, for example in a soldering oven, along the junction between the surface of the edge 120 and the outer surface of the inner ring 104. By using solder paste, the bonding material can be applied in areas that after bonding the blades to the inner ring by tongues are not normally accessible.
  • the vanes 106 include notches 130 that extend along the outer edge 103 of the vanes. are arranged. In particular, the notches are along the segment 120 of FIG Outside edge arranged.
  • the notch 130 creates an interruption along the junction between the segment 120 and the outer surface of the inner ring. The interruption prevents the capillary action along the joint and thus the further flow of the bonding material.
  • the notch creates a portion or segment 120 that is so far away from the outer surface of the inner ring 104 that the flow of the bonding material along the channel formed between the edge 120 and the inner ring 104 is prevented.
  • the bonding material does not connect the blade 106 to the notch 130 with the outer ring. That is, the bonding material does not firmly bond the segment 120 and the inner ring 104 over the entire length.
  • notch 130 is not limited to the size, shape, orientation, or location shown in the figures on the segment 120, and that other sizes, shapes, orientations, or locations on the segment 120 are within the spirit and scope of the claimed invention. It should also be understood that more than one notch 130 may be attached to the segment 120. Further, it should be understood that a turbine may include vanes 106 having different notches 130. That is, not every blade has the same notch type 130 or the same number of notches 130.
  • the turbine 100 includes one or more vanes 106 that are not connected at points to the inner ring 104 that are distributed throughout the inner ring.
  • the notch 130 changes the resonant frequency of a turbine due to the different application of the bonding material.
  • the turbine 100 is more flexible, such that the turbine generates less noise.
  • the tongues 108 and 118 which are integral with the vanes 106, provide a means for connecting the vanes 106 to the inner ring 104.
  • the tongues 108 located on the edge 120 of the vanes 106 are in the turbine 100 near the inlet side 110 arranged and inserted through slots 114, which are also located near the inlet side 110 of the inner ring 104. After insertion through the slots 114, the tongues 108 are bent over and serve to support the blades 106 on the front or outer surface of the inner ring 104.
  • the tabs 118 are disposed on the blades 106 near the outlet side 112 of the turbine 100.
  • the tabs 118 may further include the blades 106 with the inner ring 104 connect and are bent after insertion through the slots 116.
  • the notch 130 is disposed in the blade 106 between the tongues 108 and 118.
  • FIG. 10 shows further details of the design of the turbine 100.
  • Fig. 11 the position of the tongues 108 and 118 before assembly of the turbine 100 in which they are not yet bent. After insertion of the tongues 108 and 118 through the slots 114 and 116, respectively, the tongues are bent over to connect the blades 106 to the inner ring 104.
  • Fig. 12 is a plan view of an inner ring 158 according to the present invention.
  • FIG. 13 is a cross-sectional view of the inner ring 158 taken along a section line 13--13 in FIG. 12.
  • FIG. 13 is a cross-sectional view of the inner ring 158 taken along a section line 13--13 in FIG. 12.
  • Fig. 14 is a perspective view of a turbine blade 151 used in conjunction with an inner ring according to the present invention.
  • the following description will be seen in conjunction with FIGS. 12 to 14.
  • the blade 151 will be used as an example in the following discussion, however, it should be understood that other turbine blades, for example the blades 106 shown in FIG. 11, may be used in conjunction with an inner ring according to the present invention.
  • the ring 158 includes slots 161 and 163 which serve to receive the tongues 153 and 155, respectively.
  • the slots 161 and 163 include flared portions 132 and 134, respectively.
  • the flared portions create an open path between the outer surface 165 of the inner ring 158 and the inner surface 139 of the inner ring 158 after the tongues 153 and 155 are inserted through the slots 161 and 163, respectively were bent towards the surface 139 down.
  • An open path is understood to mean that there is a cavity or opening that connects surfaces 165 and 139 together and includes an interruption or opening in surface 165.
  • the portions 132 and 134 form an interruption in the junction between the edge 157 and the surface 165.
  • the interruption inhibits the capillary action along the joint and inhibits the flow of the bonding material.
  • the flared portions create corresponding portions of the edge 157 that are far enough away from the surface 165 to inhibit the flow of bonding material along the channel formed between the edge 157 and the surface 165.
  • the joining material does not connect the blade 151 to the outer ring at the extended portions.
  • the portions 132 lie at the end of the slot 161 that faces away from the outer edge 167 of the inner ring 158.
  • the portions 134 lie at the end of the slot 163 that faces away from the inner edge 169 of the inner ring 158.
  • slots 161 and 163 in Fig. 12 are each shown with extended portions, it should be understood that other configurations and combinations of portions 132 and 134 are within the spirit and scope of the claimed invention.
  • extended portions 132 or 134 may be disposed in pairs on inner ring 158, as shown in FIG. 12, or alternatively (not shown), inner ring 158 may include portions 132, portions 134 only, a combination of portions 132 and 134, or combinations slits with and without sections 132 or 134.
  • sections 132 and 134 are not limited to the size and shape shown in the figures. Of fundamental importance is that the sections are dimensioned and arranged sufficiently in relation to the respective turbine blades secured to the inner ring to provide an interruption to the capillary action of the particular connecting material used.
  • the location where the bonding material is applied to the inner ring affects where the edge 157 is joined to the surface 165.
  • the solder paste applied near outer edges 167 and 169 flows along the channel formed between edge 157 and surface 165 to slots 161 and 163, respectively, until the paste reaches portions 132 and 134, respectively.
  • the solder paste in the channel formed by edge 157 and surface 165 no longer flows due to the cavity on surface 165 resulting from the open paths at the widened portions. That is, a wall of the channel needed to continue the solder paste by capillary action is missing at the extended portions, and the capillary action is inhibited.
  • the bonding material does not connect the surface 165 with the portion of the edge 157 located between the portions 132 and 134. Due to the absence of the fixed connection between the blade 151 and the inner ring 158, the turbine is not as rigid as a turbine in which the entire edge 157 is fixedly connected to the outer surface of the inner ring.
  • Fig. 15 is a plan view of an inner ring 171 according to the present invention.
  • the following description will be seen in conjunction with FIGS. 14 and 15.
  • the vane 151 will serve as an example in the following discussion, however, it should be understood that other turbine vanes may be used in conjunction with an inner ring according to the present invention.
  • the ring 171 includes slots 173 and 175 which serve to receive the tongues 153 and 155, respectively. Between the outer edge 179 and the inner edge 181 of the inner ring 171 openings 177 are arranged.
  • the openings 177 provide an open path between the outer surface 183 of the inner ring and the inner surface (not shown) of the inner ring after the blades 151 are attached to the ring 171 (after the tongues 153 and 155 are inserted through the slots 173 and 175, respectively) Inside surface were bent over).
  • the edge facing the surface 183 that is, the edge 157
  • the orientation is perpendicular to the surface 183. That is, the edge 157 comes to lie over the opening.
  • the opening 177 forms an interruption of the junction between the edge 157 and the surface 183.
  • the interruption inhibits the capillary action at the joint and inhibits the further flow of the bonding material.
  • the openings create corresponding portions of the edge 157 that are so far away from the surface 183 that the flow of the bonding material along the channel formed between the edge 157 and the surface 183 is prevented.
  • the connecting material does not connect the blade 151 at the openings with the outer ring.
  • the openings are not limited to a particular location on the inner ring 171.
  • the openings may be midway between the slots or more near one or the other slot.
  • One and the same inner ring may have openings at various locations with respect to the corresponding slots. Besides, can not (not shown) a ring 183 corresponding slots 173 and 175 without an intermediate opening 177 have.
  • alternative means may be used, for example, the application of pins, beads, pockets or other obstacles between the surface of the inner ring and the mounting surface of the turbine blade.
  • a turbine is not limited to the use of a specific combination of inner rings and blades.
  • a turbine may use an inner ring 158 or 171 with vanes 106.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

La présente invention concerne généralement un convertisseur de couple qui comprend les éléments suivants : une bague interne ; une aube de turbine qui est connectée à la bague et qui présente un bord extérieur avec un segment qui s'applique en face d'une surface extérieure de la bague et qui est disposé à proximité de la surface extérieure ; et un matériau de connexion qui relie moins de la totalité du segment à la surface extérieure. Le segment est connecté fixement, pour réduire les effets de résonance dans la turbine. Selon certains aspects de l'invention, la bague contient une surface intérieure qui est opposée à la surface extérieure et une voie libre entre les surfaces. La présente invention comprend en général une aube de turbine entaillée et une bague interne avec une interruption dans une surface extérieure, l'interruption étant disposée de telle sorte qu'elle supprime tout effet capillaire d'un matériau de connexion coulant qui serait introduit entre une aube de turbine montée sur la bague et la surface extérieure. En outre, l'invention concerne généralement un procédé de commande de la résonance d'une turbine dans un convertisseur de couple.
PCT/DE2007/000980 2006-06-08 2007-05-31 Convertisseur de couple avec turbine brasée WO2007140751A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112007001236T DE112007001236A5 (de) 2006-06-08 2007-05-31 Drehmomentwandler mit gelöteter Trubine
JP2009513544A JP2009540224A (ja) 2006-06-08 2007-05-31 トルクコンバータ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US81202106P 2006-06-08 2006-06-08
US60/812,021 2006-06-08

Publications (2)

Publication Number Publication Date
WO2007140751A2 true WO2007140751A2 (fr) 2007-12-13
WO2007140751A3 WO2007140751A3 (fr) 2008-02-28

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PCT/DE2007/000980 WO2007140751A2 (fr) 2006-06-08 2007-05-31 Convertisseur de couple avec turbine brasée

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Country Link
US (1) US7918645B2 (fr)
JP (1) JP2009540224A (fr)
DE (1) DE112007001236A5 (fr)
WO (1) WO2007140751A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013202661B4 (de) 2012-03-01 2023-12-21 Schaeffler Technologies AG & Co. KG Drehmomentwandler mit einem Turbinenkolben
DE102014206197A1 (de) 2013-04-17 2014-10-23 Schaeffler Technologies Gmbh & Co. Kg Turbinenbaugruppe für einen Drehmomentwandler mit einer Zungenplatte und einem Turbinengehäuse, die zusammengelötet sind, und Verfahren zum Bilden derselben
US9540937B2 (en) 2014-02-04 2017-01-10 Fca Us Llc Stator for torque converter
DE102015205886A1 (de) 2014-04-23 2015-10-29 Schaeffler Technologies AG & Co. KG Drehmomentwandler-Antriebsbaugruppe mit einer an das Turbinengehäuse angenieteten Federhalterung
US10267398B2 (en) 2014-09-23 2019-04-23 Schaeffler Technologies AG & Co. KG Torque converter including axially movable turbine and friction material bonded to diaphragm spring
US9816564B2 (en) 2014-10-31 2017-11-14 Schaeffler Technologies AG & Co. KG Spring retainer including rivets for driving springs in a torque converter damper
US9611924B2 (en) 2014-11-07 2017-04-04 Schaeffler Technologies AG & Co. KG Turbine shell including recesses for recieving turbine blade tabs

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5113654A (en) * 1988-09-29 1992-05-19 Kabushiki Kaisha Daikin Seisakusho Securing structure and method of blade for torque converter
DE10257349A1 (de) * 2002-12-06 2004-06-24 Zf Sachs Ag Hydrodynamischer Drehmomentwandler
DE102004006027A1 (de) * 2003-02-14 2004-09-09 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Gelötetes Aluminiumturbinenrad für ein Kraftfahrzeuggetriebe und Verfahren zu dessen Herstellung
DE102004055295A1 (de) * 2003-11-19 2005-06-02 General Motors Corp., Detroit Hydrogeformtes Fluidkupplungselement eines Drehmomentwandlers

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS526420B2 (fr) * 1972-12-30 1977-02-22
JPS59103951U (ja) * 1982-08-12 1984-07-12 株式会社大金製作所 トルクコンバ−タ又は流体継手のブレ−ド取付け構造
US4868365A (en) * 1988-06-06 1989-09-19 Ford Motor Company Method for welding torque converter blades to a housing using a laser welding beam
US5282362A (en) * 1992-08-31 1994-02-01 General Motors Corporation Reduced leakage torque converter turbine and impeller
US5587092A (en) * 1995-05-02 1996-12-24 Borg-Warner Automotive, Inc. Method of welding vanes into a shell for a torque converter
DE19539814C2 (de) 1995-10-26 1999-08-12 Mannesmann Sachs Ag Hydrodynamischer Drehmomentwandler mit Stabilisierungsring an den Schaufelrädern
JP3884119B2 (ja) * 1997-01-10 2007-02-21 株式会社エクセディ トルクコンバータのインペラシェル
DE19845691A1 (de) 1998-10-05 2000-04-06 Mannesmann Sachs Ag Pumpenradanordnung und Turbinenradanordnung für einen hydrodynamischen Drehmomentwandler
US6282785B1 (en) * 1999-06-28 2001-09-04 Ford Global Technologies, Inc. Torque converter blades brazed to a housing using a magnetic heating process

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5113654A (en) * 1988-09-29 1992-05-19 Kabushiki Kaisha Daikin Seisakusho Securing structure and method of blade for torque converter
DE10257349A1 (de) * 2002-12-06 2004-06-24 Zf Sachs Ag Hydrodynamischer Drehmomentwandler
DE102004006027A1 (de) * 2003-02-14 2004-09-09 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Gelötetes Aluminiumturbinenrad für ein Kraftfahrzeuggetriebe und Verfahren zu dessen Herstellung
DE102004055295A1 (de) * 2003-11-19 2005-06-02 General Motors Corp., Detroit Hydrogeformtes Fluidkupplungselement eines Drehmomentwandlers

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US20080044285A1 (en) 2008-02-21
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DE112007001236A5 (de) 2009-02-19
US7918645B2 (en) 2011-04-05

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